JP2021530636A - Coupler - Google Patents

Abstract

An excavator coupler 10 having a housing with an upper portion 12 to be attached to the excavator arm and a lower portion 18 to be attached to the accessory, the lower portion being a front jaw 22 for receiving the first mounting pin 122 of the accessory and a second. A rear pin receiving area 26 for receiving the mounting pin 134 of 2 is provided, and the coupler fixes the actuator 40 and the second mounting pin 134 to the rear pin receiving area 26 and pulls the first mounting pin 122 into the front jaw 22. A state in which the first closing mechanism 30 having a movable second pin engaging surface, the second closing member 74 holding the front mounting pin 122 on the front jaw 22, and the second closing member 74 are opened. It comprises a front latch control component that controls between and closed, and the actuator 40 comprises a release member 86 for engagement with the release arm 152.

Description

The present invention relates to a coupler for connecting an accessory to an excavator arm of an excavator. One such accessory can be an excavator bucket.

Couplers, also known as quick couplers, quick hitches, or excavator couplers, for connecting accessories to the excavator arm of an excavator are known in the art. Couplers typically have an upper semifield that can be connected to the excavator arm using two mounting pins (via the two pairs of holes provided for these mounting pins) and two additional mounting pins. The accessory is equipped with a lower half body for engaging. In current couplers, the lower semifield typically comprises two jaws rather than holes. These jaws engage with each of these two additional mounting pins of the accessory and are provided with at least one closing mechanism for these jaws, typically operating a remote-controlled actuator such as a screw drive or an excavator. It is driven by a hydraulic cylinder that can be operated from the table.

A common feature of many of these couplers is that one of the two jaws is commonly referred to as the front jaw. Its opening (for receiving the first or front pin of the two mounting pins of the accessory) is generally oriented away from the first end of the coupler. This first end is commonly referred to as the front end because the end is the end that is first guided onto the accessory pins. The facing direction of the opening, the forward direction, is used to attach the coupler to the end of the excavator arm, so it is approximately parallel to the virtual line connecting the two pairs of holes in the upper half of the coupler. It is extending. The direction in which the opening faces may be tilted slightly upwards from the imaginary line, perhaps up to an angle of up to 15 degrees from the parallel line, but in many cases that direction is relative to the imaginary line. It is almost parallel.

The second jaw is then located on the bottom wall of the coupler, but on the opposite side of the coupler, near the rear end, and is therefore commonly referred to as the rear jaw. The rear jaws generally open downwards, that is, approximately perpendicular to the front jaws or to the virtual line between the two pairs of holes in the upper half of the coupler. The rear jaws may also be vertically offset, optionally up to 15 degrees.

The jaws appear to be a single object from the side of the coupler, but in many cases the jaws are bifurcated (especially to the rear jaws), and these operating mechanisms if there is an operating mechanism inside the coupler. Should be maintainable in many cases. Generally, these jaws are integrally formed with the body of the coupler, but these jaws can also be made of steel, which is harder than the body of the coupler, and will be coupled during the manufacture of the coupler. ..

In connection with the object of the present invention, the rear jaw and the front jaw are referred to even if each jaw has one or more elements.

The rear jaw generally comprises a closing mechanism with a latch member and an actuator. For most couplers, the latch member is described as a hook or closure plate. The latch member can slide or swivel between the latch position and the latch release position by using an actuator. In the latch position, the rear jaw opening is at least partially closed by the latch member. In the unlatch position, the latch member is pulled out of the latch position to keep the jaw opening open, if necessary, so that the accessory second attachment can be placed within the jaw opening. .. This may be a full pull-in to completely open the rear jaw opening, or the jaw opening is only partially obscured and is required in the latch position for certain accessories. The pull-in may not be complete (various accessories may have different pin spacings and therefore often have some variation in latch position during use of the coupler).

The latch release position is for allowing the second mounting pin to be inserted upward into the rear jaw and for the pre-captured mounting pin to be detached downward from the jaw.

Insertion or removal of the second mounting pin is usually performed by rotating the coupler to lower or lift the rear jaw relative to the front jaw. During this process, it is best to pre-place the accessories on the ground to prevent them from falling off the coupler.

As mentioned above, sometimes it is sufficient to pull the latch member out of the path of the mounting pin rather than pulling it all the way out of the jaws.

In many cases, secondary locking devices are provided on these couplers. For example, the coupler of Patent Document 1 is characterized by a block bar configured to fall into a block position in front of a latch member, in this case a pivot latch hook, under the influence of gravity. At the block position, the block bar unlatch the latch hook, even when responding to the operation of the hydraulic ram as provided for the above purpose by blocking the path of the hook from the latch position to the unlatch position. To resist. The block bar achieves such an arrangement when the coupler is in the normal use orientation of the coupler, that is, in the orientation that is hardly inverted.

The block bar is mounted so that it can swivel around the swivel axis. The swivel shaft is located near the front jaw. Therefore, the block bar is generally oriented from the swivel axis towards the rear jaw, and the coupler is upside down or partially flipped so that gravity normally urges the block bar towards its block position. Rather than, it is balanced around the swivel axis while the coupler is in its normal use orientation. Subsequently, in order to unblock the latch hook (to disconnect the accessory from the coupler), the coupler needs to be flipped, or some form of lifting the block bar from the block position to the non-block position. It is necessary to provide a means of urging. One such urging means may be a small hydraulic ram.

German Patent Application Publication No. 2330570

Due to the composition of the elements of the various moving components in these couplers, the latching and unlatching movements for attaching or detaching accessories (at the ends of the excavator's arm) to the coupler Typically, it needs to be performed using a series of default steps, in which the mechanical designs can work together for the latching or unlatching process. This is important to prevent accidental removal or to ensure proper installation-improper installation can lead to unexpected removal or damage to coupler components. Provided is a system that includes a coupler or coupler that allows both jaws to be secured to their respective pins, but can use a simpler or more undeniable set of default steps for installation and removal procedures. At the same time, it is desirable to maintain a safe fixing and holding process for accessories, a safe removal process, and even a safe installation in the event of a "pin mistake" in either the front or rear jaws. There is.

According to the first aspect of the present invention, the excavator coupler is attached to the upper part for attaching the excavator to the excavator arm and to the accessory for the excavator such as the excavator bucket. A housing is provided with a lower part for receiving a front jaw open at the front of the coupler for receiving the first mounting pin of the accessory, and a lower part for receiving the second mounting pin of the accessory. It has an open rear pin receiving area at the bottom of the coupler,
The coupler is also
A first closing mechanism for the rear pin receiving area, which is movable to secure the actuator and the second mounting pin to the rear pin receiving area and to pull the first mounting pin into the front jaw of the coupler. A first closing mechanism comprising a second pin engaging surface,
A second closing member for the front jaw to selectively hold the front mounting pin inside the front jaw,
A front latch control member for selectively controlling the second closing member to either an open configuration or a closed configuration,
Is equipped with
The actuator comprises a release member extending towards the front of the coupler for selectively engaging the release arm with the front latch control component to activate or deactivate the front latch control component. An excavator coupler is provided.

Preferably, the rear pin receiving area is a rear jaw that opens to the bottom of the coupler.

Preferably, the bottom wall of the front jaw has a lip at its free end.

Preferably, the rear pin receiving area comprises a lip at its free end.

Either or both of these lips can help prevent the release of each first or second mounting pin from each jaw or pin receiving area.

The lip preferably defines an upward angled slope that resists the pin coming out of the gripped state.

Preferably, the rear pin receiving area is angled to connect to the free end of the rear pin receiving area so that the second mounting pin is forced to engage the rear pin receiving area when the two pins are clamped to the coupler by an actuator. It has a slope.

Preferably, the angled slope is combined with the lip to define the indentation, or the angled slope and lip have a second mounting pin of the accessory inside when the first closing member is retracted. They are spaced far enough apart to define the displaceable recesses, and the accessory pins need to be lifted from the recesses to open the lip.

Preferably, the actuator is a hydraulic ram with a cylinder and piston.

Preferably, the movable second pin engaging surface is part of the latch. Preferably, the latch is a swivel hook. The latch may be a sliding plate or jaw.

Preferably, the cylinder is attached to a latch and the free end of the piston is attached to the housing of the coupler. Alternatively, the free end of the piston is attached to the latch and the cylinder is attached to the housing.

Alternatively, other forms of actuators such as pneumatic actuators and screw driven actuators can be used.

Preferably, the latch hook swivels around a predetermined axis within the coupler housing.

Preferably, the second latch member is rotatably attached to the housing around the second axis. Preferably, the second shaft is located above and in front of the rear wall of the front jaw. Preferably, the second shaft is placed in front of the mounting pin if it fits into the rear of the front jaw.

Preferably, the second latch member is spring-loaded to a default (default) latch position.

Preferably, the second latch member has a predetermined range of motion on both sides of the predetermined latch position. Preferably, the range is between the more closed and open states.

Preferably, the release arm can selectively move the second latch member to the open state or release the second latch member to a predetermined position (initial setting position).

Preferably, the first mounting pin can move the second latch member to a more closed position if it can hang from the second latch member.

Preferably, the more closed position is the position where the latch bar of the second latch member faces the lip of the front jaw.

Preferably, in the more closed state, the release surface of the second latch member is moved to a position beyond the reach of the release arm, whereby the second latch member is opened to the predetermined latch position or in the closed state. It is a state in which the release arm cannot open the second latch member until it returns to the position between the states.

Preferably, when the second latch member is in a more closed state, the release arm is positioned above the second latch member when fully engaged by the release member, at which point the release arm , Prevents the second latch member from opening.

Preferably, the second latch member is urged to its default latch position by a bidirectional spring-so that it is either more latched or open-in both directions of the second latch member. Can be moved.

Preferably, the spring is a roster-type spring with an inner bar and outer casing, each having a square section, and elastic members at the corners of the outer casing. It should be noted that conventional coil springs can be similarly operated to achieve this purpose.

Preferably, the roster spring has the shaft of the second latch member rotatably fixed to the latch bar of the second latch member and forms the inner bar of the roster spring, the outer casing being the housing of the coupler. It is a spring that is rotatably fixed.

Alternatively, the roster spring is such that the outer casing of the roster spring is rotatably secured to the latch bar of the second latch member and the shaft is rotatably secured to the coupler housing. It is a spring.

Preferably, the outer casing has an integral structure.

Preferably, the roster spring provides a rotation angle of about 60 degrees between one upper limit and the other upper limit.

The second latch member may have a flange or surface on it, the flange or surface interacting with the stopper surface 46 in the coupler housing 88 to limit the rotational movement of the second latch member 74. However, it will probably be possible to achieve a degree of rotation of only 40 to 90 degrees. In this embodiment, the degree of rotation from completely blocking to fully opening is about 60 degrees. This prevents the roster spring from rotating too much, or, if provided instead, the conventional spring from stretching too much.

Preferably, the fully open state of the second latch member brings the bottom edge of the second latch member substantially parallel to the upper wall 42 of the front jaw, preferably identical to the upper wall 42 of the front jaw. Bring on or above a plane.

Preferably, the lowermost edge of the second latch member rotates downward to a predetermined state in a more closed state that defines an angle of 60 degrees with the upper wall. The default latch position is preferably 30 degrees. An angle of 20 to 50 degrees may be selected from the fully open position.

Instead of 30 degrees, other angles can be achieved, depending on the amount of twist required to open the jaws-the deforming member provides additional resistance to torque, the inside of which is compared to the outside. Rotate more.

For more closed positions, this may be 30 to 80 degrees from the fully open position.

Preferably, the second latch member is provided with a curved free end face, which surface is where the first mounting pin is freely removed from the rear of the front jaw and comes into contact with the second latch member. , Engage with the first mounting pin. The curved free end face can help receive the mounting pins in a partially cup fashion.

The bottom wall of the front jaw preferably has a recess for accommodating a portion of the mounting pin when it can be lifted from the rear of the front jaw.

Preferably, the latch bar of the second latch member extends substantially radial from its swivel axis.

Preferably, the release surface engaged by the release arm is provided on the flange of the second latch member, which preferably extends substantially radial from the swivel axis of the second latch member. ..

Preferably, a groove or recess is provided between the latch bar and the flange.

Preferably, the free end of the release arm is sized to fit loosely into a groove or recess to access the release surface of the flange.

Preferably, the release arm separates from the flange when the second latch member is in a more closed state to access the back side of the flange when the second latch member attempts to return to the open state.

Preferably, the front latch control component has a second arm located behind the release member, which provides the release member when the release arm is engaged to the back side of the flange. It is supported and prevents the second latch member from being lifted to the open state.

Preferably, the release member has a protrusion on its side surface, which protrusion has a front surface in contact with the release arm.

The protrusion also has a rear surface that contacts the second arm to prevent the second latch member from being lifted to the open state when the release arm is above the back side of the flange. Since the protrusions also extend laterally, the side protrusions are used so that the release arm can be separated from the side surface of the cylinder 40.

Preferably, the front latch control component is a swivel component that is preferably mounted on the same axis as the piston, i.e., on the piston pin. Preferably, the release arm, and the second arm, extend radially outward from the axis of the swivel component.

The present invention is also an excavator coupler.
A housing comprising an upper part for attaching the excavator to the excavator arm and a lower part for attaching to accessories for the excavator such as an excavator bucket, the lower part being the first of the accessories. A housing with a front jaw open at the front of the coupler to receive one mounting pin and a rear pin receiving area open at the bottom of the coupler to receive the second mounting pin of the accessory.
A first latch member for the rear pin receiving region, the first latch member comprising an actuator for moving the first latch member between the latched and released states.
A second latch member for the front jaw, the second latch member comprises a hub attached for axial rotation about its axis, the hub being of the second latch member. A second latch member with a rostered spring such that the lock arm aligns the hub to a predetermined lock position extending at least partially across the opening of the front jaw.
Provide an excavator coupler equipped with.

Preferably, the hub is provided as a tube or barrel on which additional components are formed, molded or mounted. The hub, tube, or barrel of the second latch member can be rotatably attached to the frame by a shaft pin-preferably the central component of the roster spring.

This second aspect may include the features of the first aspect of the present invention.

The roster spring preferably comprises a pin having a square section along at least a portion of its length, the square section having a variable relative angle of rotation (by default) to the outer surface of the inner square. It is mounted inside a larger square tube or structure with a relative angle of rotation of about 45 degrees), and elastically deforming members are provided at the four corners of the larger square. The elastically deformed member carries the outer surface of the square section of the pin and the inner corner of the larger square section, whereby the square section of the pin and the larger square section are opposed to each other by compression and shearing of the deformed member. It can rotate and the resulting return urging force acts to return the two square members to the default 45 degree configuration.

The outer squares may be formed by square section components or by attaching the sides of the three squares to a flat surface.

In alternative structures, triangular sections or polygonal sections with four or more sides may be used instead. It should be noted that the four sides have been found to be the most effective solution for the second latch member having the desired angle of rotation of about 60 degrees (30 degrees in both directions from the default position).

Preferably, the shaft of the pin is fixed to the coupler housing.

Preferably, the upper wall of the rear pin receiving area is convexly curved around the central portion of the rear pin receiving area when viewed from the side of the coupler, and the first latch member is a swivel latch member. Preferably, the radial center of the curved portion of the ridge hits the hinge axis of the swivel latch member.

Preferably, the front jaw has a recess in its bottom surface, along with a lip at its free end, whereby the first mounting pin of the accessory descends into the recess if it is in the jaw. It can then be required to be lifted out of the recess in order to exit beyond the lip.

A problem that can occur with couplers is a failure of the hydraulic section. Since the hydraulic system of the actuator is generally provided with a no-return valve, a failure of the hydraulic section simply causes the coupler to lock out. Nevertheless, a situation may occur in which the pressure drops in the hydraulic section, such as when a crack occurs in the cylinder casing, and the piston may be unintentionally pulled into the cylinder. In such a situation, if the coupler is properly oriented, the weight of the accessory theoretically pulls the two mounting pins forward and lifts the front mounting pins forward from the rear of the front jaw. If the piston is unnoticed further pulled into the cylinder, the latch hook may eventually release the rear mounting pin, which causes the situation in FIG. In this situation, the accessories are still secured to the coupler by the front jaws, so that they will not fall out of the coupler, but to prevent or resist accidental contraction of the piston into the cylinder. In addition, it is still desired to create a backup for the hydraulic section.

According to the third aspect of the present invention, it is an excavator coupler.
A housing comprising an upper part for mounting the excavator on the excavator arm and a lower part for mounting on accessories for the excavator such as an excavator bucket, the lower part being the first of the accessories. A housing with an open front jaw at the front of the coupler to receive the mounting pins of the accessory and an open rear pin receiving area at the bottom of the coupler to receive the second mounting pin of the accessory.
A first latch member for the rear pin receiving region, the first latch member comprising an actuator for moving the first latch member between the latched and released states.
Is equipped with
The actuator is a hydraulic actuator with a cylinder and a piston.
An excavator coupler is provided in which an elastic drive (sprung driver) is provided inside the piston to urge the piston in an extended state with respect to the cylinder.

Preferably, the elastic drive is a pneumatic piston.

Preferably, the elastic drive comprises a casing mounted within the piston and a rod extending from the casing and beyond the piston into the void of the cylinder.

Preferably, the cylinder has a head at the proximal end of the cylinder and the piston extends from the distal end of the cylinder. Preferably, the rod is attached to the head, the end wall of the cylinder at the proximal end of the cylinder.

Preferably, a protective sleeve surrounds the rod. Preferably the sleeve has an open end sized to accommodate the casing.

A seal is provided between the rod and the casing so that when the rod is press-fitted into the casing, internal pressure is created in the casing and a restoring force is provided to the rod so that it is in an extended state.

Preferably, the seal is provided between the casing and the end of the piston, or the inner wall of the hole in which the piston is located.

Alternatively, the seal is provided between the inner wall of the hole in which the piston is located and the protective sleeve.

Preferably, an additional seal is provided between the protective sleeve and the casing when the end of the casing closest to the proximal end of the cylinder is located within the protective sleeve.

In an alternative embodiment, the casing is formed as part of the piston, the rod extends from the proximal end of the piston and is sealed against the inner wall of the hole in which the rod is located. Creates a gap in the piston distal to the rod, which provides a compressive return force to the rod after it is pushed into the piston.

In an alternative embodiment, the proximal end of the casing is attached to the head of the proximal end wall of the cylinder, and the rod extends from the distal end of the casing to the inside of the piston hole, preferably. The free end of the rod is attached to the piston, preferably at the end of the rod.

Preferably, the distal end of the piston is also located within a hole in the piston, which is larger than the diameter of the rod. A seal can be provided on the inner wall of the hole in which the piston is located or at the entrance of the piston.

The seal helps prevent the hydraulic fluid that drives the piston from entering the hole in the piston or into the casing.

If the elastic drive is a pneumatic piston, the seal also allows air or gas from the pneumatic piston or air or gas in the hole around the rod or casing or in the protective sleeve around the rod / casing to enter the hydraulic fluid of the cylinder. To prevent.

In an alternative embodiment, the elastic drive is attached to the side of the cylinder, preferably to a part connected to the wall of the cylinder.

Preferably the side surface is the lower surface of the cylinder.

A protective sleeve may be re-installed to protect the rod-because the rod is relatively thin, the protective sleeve increases the radius of the moving part to provide resistance to buckling of the elastic drive.

In this alternative embodiment, it is preferred that the free end of the elastic drive is swivelably attached to a flange at its distal end, the proximal end being within the part.

The compressed gas of the pneumatic piston may be contained both inside the casing and outside the end of the casing, and the object to which the casing is attached provides an extension of the gas cavity. This allows shorter casings to be used.

Preferably, the gas cavity is connected to a supply line that allows selective repressurization of the gas cavity. This makes the product a maintainable component and can correct pressure loss after a period of use.

Here, these and other features of the present invention will be described in more detail with reference to the accompanying drawings, as merely examples.

It is a figure which shows typically the internal operation of an example of the coupler based on this invention in the accessory latch state in the state which two attachment pins of an accessory are fixed in two jaws of a coupler. The first mounting pin of the accessory is freely removable from the front jaw of the coupler but is inside the front jaw and the second mounting pin is ready to move into or removed from the rear jaw of the coupler. It is a figure which shows schematic the internal operation of the coupler of FIG. 1 in the state of being released an accessory. The first mounting pin of the accessory is locked in the front jaw of the coupler, and the second mounting pin is ready to move into or removed from the rear jaw of the coupler. It is a figure which shows schematic the internal operation of the coupler of FIG. 1 in an appropriate release state. It is a figure which shows the hydraulic cylinder for the coupler based on the further aspect of this invention. It is a figure which shows the hydraulic cylinder for the coupler based on the further aspect of this invention. It is a figure which shows a different hydraulic cylinder for a coupler based on a further aspect of this invention. It is a figure which shows a different hydraulic cylinder for a coupler based on a further aspect of this invention. It is a figure which shows another different hydraulic cylinder for a coupler based on the further aspect of this invention. It is a figure which shows another different hydraulic cylinder for a coupler based on the further aspect of this invention. It is a figure which shows the alternative structure of the hydraulic cylinder for the coupler based on the 3rd aspect of this invention. It is a figure which shows the alternative structure of the hydraulic cylinder for the coupler based on the 3rd aspect of this invention. It is a figure which shows the detail of the spring member of the latch of the front jaw of a coupler, and the preferable form of a roster type spring. It is a figure which shows the operation of a roster type spring. It is a figure which shows the operation of a roster type spring. It is a figure which shows the operation of a roster type spring. It is a figure which shows an example of the center pin of the roster type spring of a coupler.

First, referring to FIG. 1, FIG. 1 shows a schematic view of the coupler 10 based on the present invention. The coupler 10 comprises a main housing 88 having an upper portion 12 and a lower portion 18. In this preferred style of coupler, as is known in the art, the top has a pair of mounting holes 44 for mounting the coupler 10 to the excavator arm of the excavator.

The lower portion 18 instead has two jaws 22 and 26, the first jaw 22 is arranged to open to the front 24 of the coupler and the second jaw 26 is the bottom 28 of the coupler 10. It is open to. The second jaw is commonly referred to as a horseshoe, but the second jaw-contains a narrower opening, a wider opening or side-for the capacity of many variable accessories. It can have a variety of shapes, so that the rear pin receiving area and the rear mounting pin 134 are wider or more spaced from the accessory front mounting pin 122, depending on the size of the accessory or the manufacturer. They may be separated at narrow intervals. Note that any given accessory generally has a fixed pin spacing, so the coupler will have very few given pins if the rear jaws are narrower to accommodate a given range of accessory sizes. It can be sized to accommodate the placement accessories.

The illustrated rear jaw 26 has a width wider than its depth to provide compatibility with a wide range of accessories, whereas the first or front jaw 22 has a first attachment. It has a depth greater than its width to provide a deeper fixation of the pin 122.

As illustrated, the rear jaw is preferably at least twice as deep as the jaw 26 in its deepest depth (ie, height).

The coupler 10 also includes a first latch member 30, a second latch member 74, and a hydraulic ram or cylinder 40. The hydraulic ram or cylinder 40 is commonly referred to as an actuator. Other forms of actuators such as pneumatic actuators or screw driven actuators can be used instead.

The first latch member 30 is for latching the second mounting pin 134 to the rear jaw 26, whereas the second latch member 74 has the first mounting pin to the first jaw 22. It is for latching 122. The hydraulic cylinder 40 is a hydraulic line not shown, which is customary in the art, for supplying power to the movement of the first latch member 30, and in this embodiment, the hydraulic cylinder 40 is hydraulic. The cylinder 40 opens a latch state in the coupler housing 88 in which the first latch member 30 secures the second mounting pin as shown in FIG. 1 and a rear jaw as shown in FIGS. 2 and 3. Therefore, the latch member 30 rotates between the release state in which the latch member 30 is pulled away from the second mounting pin. In this embodiment, this is achieved by rotating the latch member 30 in a direction such that the lower portion moves toward the front of the coupler 10.

The coupler also includes a swivel pin 98 for the second latch member 74 to swivelly mount the second latch member 74 above and in front of the fitting position for the first mounting pin 122. Thus, similarly, the second latch member has a fixed shaft with respect to the coupler housing 88.

A piston pin 102 extending between the side walls of the coupler and substantially parallel to the two mounting pins 122, 134 to swivelly attach the distal end of the piston 104 of the hydraulic cylinder 40 to the coupler housing 88. Is also provided. Subsequently, the head 112 of the cylinder 40 is rotatably attached to the first latch member 30 by one or more pins 114 so that the hydraulic cylinder is the first latch member-in this case the latch hook. -Can be moved. In an alternative embodiment, the cylinder and piston may be reversed such that the head 112 of the cylinder 40 is fixed to the housing 88 and the distal end of the piston 104 is instead attached to the first latch member 30.

The actuator, in this example the cylinder 40, has a front latch actuating member 36 extending forward from the cylinder 40. The front latch actuating member 36 is provided for interaction with a second latch member 74-indirectly in this embodiment. In this embodiment, this is achieved by the free end of the front latch actuating member 36 that engages the release arm 152, which subsequently interacts with the second latch member 74. For this purpose, there is a flange 80 provided on the second latch member 74, in which the second latch member has a default latch position as shown in FIG. 1 and an opening as shown in FIG. The release arm 152 has a release surface 82 that can be contacted when in any position between the two states, and the continuous movement of the front latch actuating member 36 in the forward direction 38 with respect to the housing 88 is release. After contacting the arm 152, it causes such contact between the release arm 152 and the release surface 82, followed by a second latch due to the urging of the release arm 152 on the release surface of the second latch member 74. It causes the resulting movement of the member 74 from its default latch position to the open state.

The second latch member can also move in the opposite direction from the default latch position of FIG. 1 towards a more closed state as shown in FIG. In such a more closed state, the free end moves forward at its bottom, the release surface 82 moves to a position beyond the reach of the release arm 152 (here below its movement line), thereby moving the release arm. The 152 can no longer interact with the release surface 82 of the flange to move the second latch member 74 into the open state. Instead, as the front latch actuating member 36 is continuously moved to a position where the second latch member 74 is opened, the release arm 152 is here at a predetermined position where its end is located beyond the flange 80. The opposite surface 136 of the flange is here the latch holding surface 136. Thus, the front latch actuating member 36 instead moves the release arm 152 to a predetermined state, in which state the release arm 152 closes the second latch member 74 in its default latch state or more. Locked to a position below the open state, such as a state-the release arm is prevented from rotating or moving further upwards, and thus by a stopper in the housing or as shown in the second swivel component 50. The arm 52 provides a locking function, and the swivel component 50 has a release arm 152 capable of stopping such further rotation instead.

In order to initialize the second latch member 74 to its predetermined latch position, a spring is provided to provide an urging force toward the predetermined latch position. This is a bidirectional spring that allows the second latch member to move in both directions-either towards a more latched state or an open state.

In this embodiment, the second latch member is rotatably mounted around its axis 98. The spring urges the second latch member 74 so that the second latch member 74 is initially set to the default latch position under the force of the spring, and in the default latch position, the second is the second latch member 74. The latch member 74 extends across the opening 58 of the front jaw 22 partially. The spring in this preferred embodiment is a roster spring. However, conventional coil springs may likewise be provided to serve that purpose, for example by being connected to the housing at one end and to the flange of the second latch member 74 at the other end. Note that roster springs provide a compact solution. In the following, the roster type spring will be described in more detail with reference to FIGS. 12 to 16.

The free end 32 of the second latch member 74 will eventually have the first mounting pin 122 when the first mounting pin 122 is attempted to be removed from its fitting at the rear 34 of the front jaw 22. Arranged to engage the second latch member, the second latch member 74 tends to rotate towards (or towards) the more closed state of FIG. ..

As is known in the art, the second latch member is a coupler housing, perhaps to limit the rotational movement of the second latch member 74 so as to allow a degree of rotation of 40 to 90 degrees or less. A flange or surface that interacts with the stopper surface 46 at 88 may be provided on the second latch member. In this embodiment, the degree of rotation between full blocking and full opening is about 60 degrees-when fully open, the bottom edge of the second latch member is the upper wall of the front jaw. In a state approximately parallel to 42 and more closed, its surface is approximately 60 degrees from its upper wall 42. Note that the default stationary position may be at a selected angle between 20 and 50 degrees from the fully open position. As shown, the angle is about 30 degrees. For a more closed position, the angle may be 30 to 70 degrees.

As illustrated in FIGS. 1 to 3, the second latch member is provided with a curved free end face 32, which is such that the second latch member 74 is more closed from its default position. Engages with the first mounting pin 122 when moved to position. The curved surface of the free end face 32 can help reduce or eliminate the stopper requirement of one of these stoppers 46-by receiving the mounting pins partially in a cup fashion, such cups can be varied with the pins. To provide an interaction angle, it is possible to achieve a two-point contact between the mounting pin and the free end face 32, which allows the cup to contact and clog the mounting pin. In that clogged state, further downward rotation of the second latch member 74 can be prevented. This can generally occur when the coupler and accessories are flipped so that the pin is placed in contact with the top wall 42 of the front jaw and the load is applied on the top wall 42. Therefore, this ensures that the exit of the first mounting pin 122 from the front jaw is blocked.

However, in FIG. 3, the coupler is not inverted so that the first mounting pin 122 is located below the front jaw 22. At the bottom, the embodiment has a recess sized to accommodate a portion of the mounting pin 122-preferably a recess 48 with at least two point contacts. This recess terminates at or in front of the lip 126 near the free end at the bottom of the jaw 22. The recess and lip accommodate the first mounting pin in the recess because the cup portion pushes the pin 122 into its recess 124 when the first mounting pin presses against the latch member and lip. It cooperates with the free end 32 of the latch member.

A cup portion 128 that pushes the mounting pin 122 into the recess 124 is shown in FIG. In this configuration, the pin 122 cannot exit the front jaw 22, and the lip bears most of the stress from the pin.

In addition to the cup portion 128, the second latch member 74 includes a body for accommodating the shaft 98 and a roster spring as described below, the body for providing a release surface 82. It features a first flange and a second flange for providing a latch bar for the front jaws. In this embodiment, the latch bar extends substantially radially from the body with respect to the shaft 98. Similarly, the first flange 80 extends substantially radially from its body. A groove or recess 84 is provided between them. During use, the release arm 152 enters the groove or recess 84 when the second latch member 74 is lifted open as shown in FIG. 2, but the first latch member moves rearward. When the cylinder 40 extends its piston 104, it falls off from the groove or recess 84. Thus, if the latch bar is subsequently moved first to its more closed state by the accessory's first mounting pin, the release arm 152 can instead pass through the original flange 80. When the release arm 152 passes through the original flange 80, the second latch member 74 until the actuator again extends the piston 104 from the cylinder 40 (and subsequently returns the release arm 152 to the position behind the original flange 80). When is attempted to be reopened, the release arm is instead positioned beyond the top of the original flange 80 to selectively engage the latch holding surface on the back 136 of the original flange 80. Moving.

With respect to the cup portion 128, the portion 128 is formed by a trailing edge of an additional flange 84, the trailing edge of the additional flange 84 being a second flange with an original flange 80 with a release surface and a latch bar and a free end 32. It is on the side of and extends between these flanges.

With respect to the actuating member 36 of the cylinder 40, the actuating member 36 includes a finger portion facing forward. There is a protrusion 86 on the side surface of the finger portion, and the protrusion 86 has a front surface in contact with the release arm 152. As a result, the protrusions also extend laterally, so that the release arm 152 can be separated from the side surface of the cylinder 40.

In this embodiment, the release arm 152 is a part of the swivel component 50, and the swivel component 50 is attached to the same shaft as the piston pin 102. The same shaft pin 102 may be used for this purpose. The swivel component 50 has a release arm 152 extending outward in a substantially radial direction from the swivel component 50, and has a second arm 52 separated from the release arm 152 in the circumferential direction. There is. There is an additional recess or groove between the release arm 152 and the second arm 52, in which the additional recess or groove is the first while the release arm 152 is engaged with the release surface 82 and the release arm 152 is first. The protrusion 86 fits while being placed on the flange 80 of the. When the piston 104 extends from the cylinder 40, the protrusion 86 exits the additional groove or recess, which allows the swivel component 50 to rotate freely.

Alternatively, the swivel component 50 defaults so that the release arm 152 is located outside the groove or recess 84 of the second latch member (in this embodiment, it is in a downwardly suspended position). Can be elastically urged to the state of.

Preferably, the release arm 152 has a lip for engaging with the release surface.

The second arm is present behind the protrusion 86 when the protrusion is engaged to the release arm 152, so that when the coupler is inverted, or the release arm is latched by the actuating member 36 or protrusion 84. It functions to prevent rotation of the swivel component 50 while the second latch member opens when moved to a position above the member.

Subsequently, referring to FIG. 3, the front mounting pin 122 is moved forward from the rear 34 of the front jaw 22. Further, the piston 104 is further pulled into the cylinder, whereby the latch hook 30 releases the rear mounting pin. In this situation, the accessory is still secured to the coupler by the front jaw so that the accessory will not fall out of the coupler. Since this situation is undesirable, FIGS. 4-11 further show optional features of this coupler designed to avoid this situation. These features will be further described below.

In the coupler of FIGS. 1 to 3, as shown in FIG. 2, the first latch member is pulled and the rear jaw 26 is opened by pulling the piston 104 into the cylinder 40 to the maximum extent. In an alternative embodiment, it is only possible not to pull the first latch member too far if the piston or cylinder is longer or the coupler is shorter. In a preferred embodiment, the front jaw latch mechanism still functions as described above. In such an embodiment, the first latch member still partially closes the rear jaw opening, even when fully retracted. However, it must be pulled forward enough to release the second mounting pin of the accessory intended for use with the coupler. Such configurations are typically compatible with a smaller number of accessories.

Subsequently, the roster type spring will be further described with reference to FIGS. 13 to 16.

The shaft 98 of the second latch member is provided with a square section 54 along a portion of its length. As shown in FIG. 16, this is the distal portion of the flange end 56. Proximal to the square section, i.e. closer to the flange end, is a circular section having a diameter approximately equal to the diagonal length of the square section 54, which ends at the flange end.

The flange end has a flat side portion so that it can be turned with a tool. The flange end fits into or in a bushing in a recess in the side wall of the coupler so that the pin rotates with respect to the housing.

The distal end 60 of the shaft 98 instead comprises a short end portion having a circular diameter smaller than the square width of the square section 54, whereby the shaft 98 has the square section 54 described below. It may be inserted so as to pass through the mount of the roster type spring component in a state where it can be operated in the roster type spring. The distal end 60 passes through the opposite side of the housing so that the shaft extends across both sides of the housing.

The distal end 60 has a groove near its free end for a circlip to hold the shaft on the opposite side of the housing-here shown within the bushing 64. The shaft is fixed between the two sides of the housing 88.

A second latch member 74 having a bifurcated body shape is attached to the square section, extending from the body to a flange 80 and a latch arm having a free end 32. Each of the two bifurcated body-shaped ends has a circular hole hole at one end and a square hole at the other end, where the circular hole is proximal to the square section of the shaft. Placed on the circular section portion of the axis, and the square section is placed on the square section of the axis. Therefore, the shaft is rotatably fixed to the body shape portion.

Between the two ends, there is a square outer frame 64 of the roster type spring and a square inner frame 66. There are four rubber inserts 68 between the two frames, each placed at each corner of the outer frame 64.

The outer frame is rotated 45 degrees with respect to the inner frame so that the gap between the inside of the outer frame and the outside of the inner frame can be substantially filled with the rubber insert 68. The rubber insert 68 is then placed in the corner gap between the frames with respect to the flat sides of the inner square frame to provide the default 45 degree position of the inner frame with respect to the outer frame. And is compressed against the corners of the outer frame or the two intersecting side walls. This allows the inner square frame to fit tightly into the square section of the shaft, providing the default latch state required for the second latch member.

Angles other than 45 degrees may be provided by using rubber inserts of various shapes.

Since the compressibility of the insert is not infinite, the roster spring can rotate without damaging the roster spring, or perhaps at angles of up to 20 to 38 degrees on either side of the default position. Preferably, the range of movement is up to 30 degrees on either side of the center.

Other angles may be realized instead of 30 degrees, depending on the amount of twist required to open the jaws-the deforming member provides additional resistance to torque, the inside relative to the outside. Rotate more.

It is not essential to have an inner frame, as the shaft can provide that function directly instead. However, it is easier to assemble if the roster springs are preformed so that the inner and outer frames have square holes in the inner frame to accommodate the shaft.

To hold the square outer frame in an orientation that is fixed to the housing 88 of the coupler, the square frame 64 is placed in the recess of the housing 88 or otherwise fixed to the housing 88.

The structure of the roster spring allows rotation of the inner frame over a particular angle with respect to the outer frame-typically up to 30 degrees in both directions by compressing the rubber element, as shown in FIG. .. Therefore, the second latch member 74 can rotate 30 degrees in both directions as illustrated.

Instead of making the outer frame a square tube, the outer frame can also be formed as three sides that attach to the flat surface of the housing 88.

As illustrated, the rostered construction of bidirectional springs allows the inner square frame to rotate relative to the outer square frame by compressing and shearing the rubber element, which compresses and shears the square section into its original block. Create a return force to return to the default state. In the present invention, this original state is the default latch state as shown in FIG.

Subsequent references to FIGS. 4 to 11 show various methods of exerting an urging force on the cylinder / piston, in which the-piston is arranged to urge the extension position with respect to the cylinder.

In FIGS. 4-9, an elastic drive or urging mechanism is provided inside the piston 104. Various solutions for this are illustrated. The first solution is shown in FIGS. 4 and 5, where a pneumatic backup piston is provided inside the actuator piston 104 and the end of the actuator piston 104 inside the cylinder 40 is in it. Has a hole 70 drilled to receive a pneumatic gas spring or piston 72. The pneumatic gas spring or piston comprises a casing 76 and a rod 78, which can be extended between the extended state shown in FIG. 5 and the contracted state shown in FIG.

Pneumatic pistons are exemplified, but other forms of elastic drive or urging mechanisms such as coil springs, or compression material springs such as rubber springs can be used. Preferably, the compression material spring, whether coil spring or compressed gas or fluid or solid, provides a restoring force during compression of the shape of the component or material device within it. Pneumatic pistons with movable rods are preferred.

In the contracted state of FIG. 4, the rod 78 is contracted into the void 90 as shown in black in FIGS. 4 and 5, thus compressing the gas in the void 90 and compressing the piston 104 into the cylinder 40. Generate a countervailing force.

In this embodiment, the void 90 extends within the head 112 of the cylinder 40 to make the shorter gas spring 72 feasible.

The void 90 contains air or gas under pressure to provide pneumatic elastic forces. Therefore, the contracted state of FIG. 4 has a higher pressure in the void 90 than the expanded state of FIG. Similarly, the free space in the hole can contain air or gas under pressure between the rod 78 and the wall of the hole, the compression of which is also when the rod is contracted into the casing 76. Will be higher. Therefore, FIG. 5 shows the default state of the rod 78, which causes the actuator to be initialized by the gas spring to be in the extended state, i.e. the piston 104 extended from the cylinder 40. It is urged and therefore the extended state locks the accessory mounting pin in the jaw of the coupler, which helps prevent the accessory from being released in the event of a cylinder 40 failure.

In this first embodiment, the casing 76 is attached to the head 112 of the cylinder 40. Therefore, the casing 76 slides inside the hole 70 of the piston 104. The seal 92 is provided at the distal end of the piston 104 to seal between the casing 76 and the hole 70 of the piston 104. This prevents the hydraulic fluid in the cylinder 40 from entering the space between the casing 76 and the piston 104 during normal use of the actuator. The seal also prevents the hydraulic fluid from entering the free space between the rod 78 and the hole 70. This avoids lockout of the gas spring (because the hydraulic fluid is incompressible). Similarly, air or gas in the free space of the hole around the rod is prevented from entering the hydraulic fluid, and thus (because the air mixed in the hydraulic fluid makes the hydraulic fluid partially compressible) of the actuator. It prevents the oil pressure from dropping.

Subsequent reference to FIGS. 6 and 7 provides an alternative but similar advantage configuration. In this second version, the pneumatic gas spring is reversed so that the casing 76 is instead mounted in the hole of the piston 104 and the rod 78 is instead mounted in the head 112 of the cylinder 40. In this configuration, as shown in FIG. 6, a protective sleeve 94 is provided so that the casing 76 can slide inward when the rod 78 contracts into the casing 76. A seal is re-installed on the end face of the piston 104 to prevent the hydraulic fluid from entering the hole and to prevent air or gas in the hole from entering the hydraulic fluid. An additional seal 110 is provided at the end of the protective sleeve 94 for sealing the casing 76. This allows the space around the casing to be switched between one free space and two enclosed spaces, and the casing is further supported as the rod is compressed into the casing, thus buckling the rod / casing. To resist.

In an alternative configuration, the protective sleeve 94 is made longer so that the casing 76 always projects into the protective sleeve 94, whereby the space around the casing is always separated from the space around the rod. Will be.

The advantage of providing the protective sleeve 94 is that by adding a radial structure to the gas spring configuration, the protective sleeve provides additional flexural rigidity and thus buckling resistance to the gas spring. Previously, rods could buckle, especially where they entered the casing.

Subsequent reference to FIGS. 8 and 9, exemplifying a third integrated gas spring in which the casing 76 is again inside the piston 104. Instead, the rod is wider and there is no protective sleeve. Further, the rod 78 is not attached here to the head of the cylinder, but is terminated with respect to the head of the cylinder.

As shown, instead of providing the casing 76 in the hole of the piston, it is possible to place the rod in the hole of the piston, whereby the piston itself provides the function of the casing. Therefore, it is believed that the casing is virtually non-functional or integrated with the piston.

In this third exemplary embodiment, the pressurized void 90 is in the tube 96 near the swivel-mounted end of the piston 104, with a threaded stopper or cork 100 lateral to the tube 96. It is connected with the hole 106 closed. With this configuration, the pressure of air or gas in the pressurized void 90 can be recompressed or refilled in the event of pressure loss. The pressure can be increased as needed.

Such refill ports can be similarly provided for the embodiments of FIGS. 6 and 7.

Similarly, in the embodiments of FIGS. 4 and 5, the head may be provided with a refilling hole to access the void 90.

Finally, with reference to FIGS. 10 and 11, alternative configurations are shown in which gas springs are instead attached to the outside of the cylinder 40 and to the sides of the cylinder 40 in the lateral structure 120. The lateral structure can be dedicated to the gas spring or can be part of the part around the cylinder from which the actuating member 36 extends.

The side structure 120 has a cavity in it for accommodating a gas spring, as shown. Again, there is a protective sleeve 94, but this time the protective sleeve 94 only provides protection for the rod 78 by placing it outside the piston, otherwise the protective sleeve 94 operates the coupler. Can be exposed to the environment. The protective sleeve 94 is no longer exposed to the hydraulics in the cylinder.

In this configuration, the gas spring 72 can operate to drive the rod 78 and the protective sleeve 94 between the contraction position of FIG. 10 and the extension position of FIG. 11, and the extension configuration is the default configuration.

The end of the rod or protective sleeve 94 can be attached to an additional flange 124 that extends radially from the piston pin 102, the additional flange 124 having a swivel connection 116 to the rod 78 or protective sleeve 94. Can be done. By being swiveled, the rod can rotate with the piston as the swivel latch hook moves. Alternatively, an additional flange rotates with respect to the piston pin 102. In the case of a sliding latch, the actuator does not need to be swiveled, so the connection may be fixed rather than swiveled instead.

The external gas spring is usually located below the cylinder. This has two advantages. First, because the space is limited to both sides of the cylinder, placing the external gas spring under the cylinder does not allow the external gas spring to further fill the lateral space. Second, by being placed under the cylinder, the accessory may be exposed to external elements during use of the accessory (once the accessory is attached to the coupler) as it closes the bottom of the coupler. No.

By using these gas elastic mechanisms inside or outside the piston of the cylinder 40, the cylinder 40 and the piston 104 can be moved by the hydraulic system of the cylinder 40 or the cylinder 40 itself, even though the cylinder 40 and the piston 104 do not have the normal holding force of the hydraulic part. The initial setting is that the first latch hook is in the latched state in the event of a failure. After noticing that the accessories are loose, the operator can safely hold the accessories for a sufficient amount of time to lower them to the floor.

Therefore, the present invention can only release the accessories attached to the coupler by following the proper procedure as shown in FIG. 2-the coupler if the coupler is used improperly. Cannot be released from.

These and other features of the invention are described above purely by way of illustration. Within the scope of the appended claims, the invention may be modified in detail.

10 Connector 12 Upper 18 Lower 22 Front jaw 24 Front 26 Rear jaw 28 Bottom 30 First latch member 32 Free end 34 Rear 36 Front latch actuating member 40 Actuator 42 Upper wall 46 Stopper 48 Recess 50 Swivel component 52 Second Arm 54 Square Section 56 Flange End 58 Opening 60 Distal End 64 Outer Frame 66 Inner Frame 68 Rubber Insert 70 Hole 72 Piston 74 Second Latch Member 76 Casing 78 Rod 80 First Flange 82 Release Surface 84 Recess 86 Protrusion 88 Housing 90 Void 92 Seal 94 Protective Sleeve 96 Tube 98 Shaft 100 Threaded Stopper 102 Shaft Pin 104 Piston 106 Side Hole 110 Seal 112 Head 114 Pin 116 Swivel Connection 120 Side Structure 122 Pin 124 Recess 128 Cup Part 134 Pin 136 Latch holding surface 152 Release arm

Claims (32)

Excavator coupler
A housing having an upper part for attaching an excavator to an excavator arm and a lower part for attaching to an accessory for the excavator such as an excavator bucket, wherein the lower part is the accessory. A front jaw opened at the front of the coupler to receive the first mounting pin of the article, a rear pin receiving area opened at the bottom of the coupler to accept the second mounting pin of the accessory, and so on. Equipped with a housing that
The coupler further
A first closing mechanism for the rear pin receiving area, the actuator and the first mounting pin for selectively fixing the second mounting pin to the rear pin receiving area and the first mounting pin of the coupler. A first closing mechanism with a movable second pin engaging surface for pulling into the front jaw, and a first closing mechanism.
A second closing member for the front jaw to selectively hold the front mounting pin within the front jaw.
A front latch control component for selectively controlling the second closing member between an open state and a closed state, and a front latch control component.
Is equipped with
The actuator comprises a coupler for selectively engaging a release arm with the front latch control component in order to activate or deactivate the front latch control component. .. The coupler according to claim 1, wherein the rear pin receiving region is a rear jaw open to the bottom of the coupler. The coupler according to claim 1 or 2, wherein the bottom wall of the front jaw is provided with a lip at its free end. The coupler according to any one of claims 1 to 3, wherein the rear pin receiving region includes a lip at its free end. The rear pin receiving area is such that the second mounting pin is forcibly engaged with the rear pin receiving area when the two mounting pins are clamped to the coupler by the actuator. The coupler according to any one of claims 1 to 4, wherein the coupler is provided with an angled slope connected to the free end of the above. The coupler according to any one of claims 1 to 5, wherein the actuator is a hydraulic ram including a cylinder and a piston. The coupler according to any one of claims 1 to 6, wherein the movable second pin engaging surface is a part of a swivel hook. The coupler according to any one of claims 1 to 7, wherein the second latch member is rotatably attached to the housing. According to claim 1, the second latch member is rotatably mounted in the housing so as to rotate around an axis arranged above and in front of the rear wall of the front jaw. The coupler according to any one of claims 8. The coupler according to any one of claims 1 to 9, wherein the second latch member is spring-loaded to a predetermined latch position. The second latch member has a predetermined movable range on both sides of a predetermined latch position between a more closed state and an open state, according to any one of claims 1 to 10. The coupler described. The second latch member has a more closed state, and in the more closed state, the release surface of the second latch member moves to a position beyond the reach of the release arm. The coupler according to any one of claims 1 to 11. When the second latch member is in a more closed state, the release arm is an end that is located above the second latch member when the release arm is fully engaged with the release member. 12. The coupler according to claim 12, further comprising a portion, wherein in this position the release arm prevents the second latch member from opening. One of claims 1 to 13, wherein the second latch member is urged to a predetermined latch position by a bidirectional spring that enables bidirectional operation of the second latch member. The coupler according to paragraph 1. 14. The coupler according to claim 14, wherein the bidirectional spring is a roster spring having an inner bar and an outer casing having square sections, respectively, and elastic members at the corners of the outer casing. .. Excavator coupler
A housing having an upper part for attaching an excavator to an excavator arm and a lower part for attaching to an accessory for the excavator such as an excavator bucket, wherein the lower part is the accessory. A front jaw opened at the front of the coupler to receive the first mounting pin of the article, a rear pin receiving area opened at the bottom of the coupler to accept the second mounting pin of the accessory, and so on. With a housing and
A first latch member for the rear pin receiving region, the first latch member comprising an actuator for moving the first latch member between a latch state and a release state.
A second latch member for the front jaw, the second latch member comprising a hub attached to rotate about its axis, the hub being said to be the second latch. Each of the roster springs has a roster spring for aligning the hub in a predetermined locking position in which the locking arm of the member extends at least partially across the opening of the front jaw. A second latch member having an inner bar and an outer casing having a square section and elastic members at the corners of the outer casing.
A coupler characterized by being provided with. The coupler according to claim 16, further comprising any one of claims 1 to 13. The shaft of the second latch member is rotatably fixed to the second latch member, and the shaft forms the inner bar of the roster type spring, and the roster type spring of the roster type spring. The coupler according to any one of claims 15 to 17, wherein the outer casing is rotatably fixed to the housing of the coupler. The outer casing of the roster type spring is rotatably fixed to the second latch member, and the shaft of the second latch member is rotatably fixed to the housing of the coupler. The coupler according to any one of claims 15 to 17, wherein the coupler is characterized by the above. The coupler according to any one of claims 15 to 19, wherein the outer casing has an integral structure. Excavator coupler
A housing having an upper part for attaching an excavator to an excavator arm and a lower part for attaching to an accessory for the excavator such as an excavator bucket, wherein the lower part is the accessory. A front jaw opened at the front of the coupler to receive the first mounting pin of the article, a rear pin receiving area opened at the bottom of the coupler to accept the second mounting pin of the accessory, and so on. With a housing and
A first latch member for the rear pin receiving region, the first latch member comprising an actuator for moving the first latch member between a latch state and a release state.
Is equipped with
The actuator is a hydraulic actuator including a cylinder and a piston.
A coupler characterized in that a pneumatic piston is provided inside the piston in order to urge the piston into an extended state with respect to the cylinder. 21. The coupler according to claim 21, wherein the pneumatic piston includes a casing mounted in the piston and a rod extending from the casing beyond the piston into the void of the cylinder. .. 21. The pneumatic piston includes a rod extending from the piston of the actuator in a state where there is an air or gas gap behind the rod in the piston of the actuator. The coupler described in. The coupler according to claim 22 or 23, wherein the rod is attached to an end wall of the cylinder. 23. The coupler according to claim 24, wherein a protective sleeve surrounds the rod and the protective sleeve has an open end sized to accommodate a casing. The pneumatic piston comprises a casing and a rod extending from the casing, the proximal end of the casing being attached to the end wall of the cylinder, and the rod being distal to the casing. It exits the end and extends into a hole in the piston, characterized in that the free end of the rod is attached to the piston at or near the free end of the rod. The coupler according to claim 21. Excavator coupler
A housing having an upper part for attaching an excavator to an excavator arm and a lower part for attaching to an accessory for the excavator such as an excavator bucket, wherein the lower part is the accessory. A front jaw opened at the front of the coupler to receive the first mounting pin of the article, a rear pin receiving area opened at the bottom of the coupler to accept the second mounting pin of the accessory, and so on. With a housing and
A first latch member for the rear pin receiving region, the first latch member comprising an actuator for moving the first latch member between a latch state and a release state.
Is equipped with
The actuator is a hydraulic actuator including a cylinder and a piston.
An elastic drive device is provided outside the cylinder in order to urge the piston into an extended state with respect to the cylinder.
The elastic drive device is a coupler characterized in that it is attached to a side surface of the cylinder. The coupler according to claim 27, wherein the side surface is a lower surface of a cylinder. 28. The coupler according to claim 27 or 28, wherein the elastic drive device is a pneumatic piston mounted in a molded product connected to an outer wall of the cylinder. The free end of the elastic drive is rotatably attached to the flange at its distal end, and the proximal end of the elastic drive is located inside the molded product. 29. The coupler according to claim 29. A protective sleeve is provided to protect the rod of the pneumatic piston.
29. The coupler according to claim 30, wherein the protective sleeve has an open end that surrounds the rod and is sized to accommodate the casing of the pneumatic piston. 21 to 26 or 29, wherein the gas cavity of the pneumatic piston is connected to a supply line to allow selective repressurization of the gas cavity. Item 3. The coupler according to any one of Items 31.

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